KR20000041603A - Structure for decreasing oil discharge of scroll compressor - Google Patents

Abstract

PURPOSE: A structure for decreasing the discharge of oil in a scroll compressor is provided to recollect oil from a compression chamber consisted of a scroll lap of a fixing and a rotating scroll without an additional device. CONSTITUTION: An oil channel(40) is prepared on an upper face of involute curved line scroll lap(30) in a compression chamber that a fixing scroll(11) and a rotating scroll make up. When an upper face of the scroll lap is plane, the oil channel is hollowed from the surface. On the other hand, when the upper end face is a tip seal, the oil channel is positioned in a non-exposed type in a tip seal groove(31) while the tip seal is contacted with a face of a counterpart side. When a passage for flowing down the oil by designating various types of the oil channels along with the involute curved line upper end face, the oil remaining on the lap surface is quickly sent to a low pressure side oil face through the oil channel. Accordingly, the amount of the vented oil is decreased.

Description

Oil discharge reduction structure of scroll compressor

The present invention relates to a device for reducing the oil discharge amount of the scroll compressor, and more specifically, the fixed scroll and the rotating scroll wrap to form a compression chamber and the refrigerant in the process of inhaling, compressing, and discharging the refrigerant by the compression force generated by their relative motion By changing the flow path of the oil flowing together to reduce the amount of oil discharged to solve the problem caused by the oil shortage.

In general, the scroll compressor is a type of compressor mainly used in air conditioners and freezers because it has excellent dynamic performance in a wide range of capacity compared to other types of compressors.

In addition, since the compression chamber is composed of scroll wraps, the upper, lower, left, and right sides of the scroll wraps exhibit contact motion. Therefore, the wear of the compression chamber is larger than that of other compressors. .

Lubrication on the contact surface as well as the scroll compressor is provided as a minimum measure to avoid wear and various mechanical defects. Scroll compressors also have contact surface around the compressor section and the upper and lower support systems of the spindle. It is designed to enable lubrication at. This lubrication system has a close relationship with the drive system of the scroll compressor and allows the dynamic movement of each drive system to be normally performed.

The main part of the scroll compressor includes a case 6 having upper and lower caps 4 and 5 to distinguish the discharge chamber 2 and the suction chamber 3 through the upper diaphragm 1 as shown in FIG. Compression chamber in the form of an electric motor 7 and a stator 8 and a main shaft 9, a rotating scroll 10 and a fixed scroll 11 interlocked with the motor mechanism, and protected by the upper diaphragm 1. Compressor spheres forming 12, etc., with the upper part being the discharge chamber 2 and the lower part being the suction chamber 3 centering on the upper diaphragm 1.

In addition, there is a check valve 13 between the upper diaphragm 1 and the fixed scroll 11 that separates the suction chamber 3 and the discharge chamber 2, through which the refrigerant gas compressed in the compression chamber 12 is discharged. (2) or prevent the back flow of gas in the discharge chamber (2).

The pressure distribution in the compressor case 6 during operation is such that the suction chamber 3, which introduces the refrigerant through the suction pipe 14, becomes the low pressure side, and the discharge chamber 2, which flows in through the compression mechanism, is relatively high pressure side. Becomes

The refrigerant flowing through the suction pipe 14 is compressed in the compression chamber 12 of the involute curve wrap (Wrap) formed on the orbiting scroll (10) receiving the driving force of the main shaft (9) and the fixed scroll (11) coupled thereto When the rotor 7 rotates and the main shaft 9 is rotated, the old dam ring 17 on the main frame 15 and the driving bush 16 is oriented in the direction of the turning scroll 10. It is connected to the key groove to change the rotational movement of the main shaft (9) to the turning movement of the turning scroll (10), the turning scroll wrap (30) and the outer wrap (30A) of the fixed scroll (11) in the initial position When the suction flow path is formed apart, the refrigerant introduced therethrough collects two half-moon compression chambers 12 formed by the two scroll wraps 30 and 30A according to the turning angle to the center of the scroll wraps 30 and 30A. Compress continuously.

Eventually, the compression chamber 12 collected at the center is opened at the discharge port 18 on the rear side of the fixed scroll 11, and the discharged compressed refrigerant gas pushes up the check valve 13 mounted on the fixed scroll 11. It is discharged into the discharge chamber 2 composed of the diaphragm 1 and the upper cap 4, and the refrigerant gas is sent to the refrigeration / air conditioning cycle such as a condenser through the discharge pipe 19.

In the compression chamber 12 formed by the fixed scroll 11 and the revolving scroll 10, leakage in the radial direction through a gap between the tip of the wrap 30 of the revolving scroll 10 and the bottom of the fixed scroll 11 is performed. And leakage may occur in a tangential direction through a gap between the side portions of the wrap 30 and 30A connected to each other. In order to prepare for such leakage, the driving bush 16 may be provided in the form of a slide bush or an eccentric bush. It is processed to provide compliance in the radial direction, or as shown in Fig. 2.3, tip seal grooves 31 and 31A are formed on the top surfaces of the scroll wraps 30 and 30A to prepare for leakage in the radial direction.

In particular, if the tip thread groove 31 is placed in the scroll wrap 30 of the turning scroll 10 and the tip thread 32 is seated therein, one side of the high pressure is formed on the border of the wrap 30 as shown in FIG. The low pressure is formed to necessarily leak the refrigerant from the high pressure side to the low pressure side, the tip chamber 32 located at the top of the wrap serves to resist the flow of the refrigerant generated from the high pressure side to the low pressure side of the wrap side Refrigerant leakage to the furnace is reduced. The same tip chamber 32 structure is applied to the fixed scroll wrap 30A, and an example of the refrigerant leakage path in the scroll wrap is shown in FIG. 6.

The scroll compressor arranges all the drive systems, that is, the compression mechanism and the power mechanism in the center of the shaft, in order to flow the refrigerant in the order of main shaft rotation, rotation scroll rotation, refrigerant suction, compression, and discharge, which is supported by the support system. The driving system is supported on the case by dividing the upper side and the lower side again.

The upper part of the compression mechanism support system is a type of supporting the pivoting scroll (9) coupled to the fixed scroll (11) and the wrap through the main frame (15) to support the main shaft (9).

There is a thrust bearing 20 on the surface where the turning scroll 10 and the main frame 15 come into contact with each other, and the driving bush 16 fitted to the main shaft 9 is made into a slide or an eccentric type and the turning scroll coupled thereto ( 10) the journal bearing 21 is provided between the tangential surface and the journal bearing 21A is inserted into the contact movement surface of the main shaft 9 and the main frame 15 to remove the fixed scroll 11 as a whole. The main frame 15 receives the dynamic load of the compression mechanism and the bearing parts are lubricated between the driving parts.

The lower support system is a portion decorated for supporting the main shaft (9). This is typical of the subframe 22 supporting the main shaft 9 on the inner wall of the case 6, and the journal bearing 21B provided on the contact surface between the main shaft 9 and the subframe 22. As shown in FIG.

In addition to the support system, there is a lubrication system. This part has the supply passage 23 under the main shaft 9 to send oil to the contact motion surface or the compression mechanism, which appears at the center of the main shaft and the support system, and ascends from here, the upper turning scroll 10 of the main shaft 9 It has an eccentric inclined feed passage 24 and several outlets up to the point where it meets), and has an oil pumping system and a return system.

The oil pumping system is centered on the subframe 22, and submerged in the oil level, and includes a supply passage 23 centered on the main shaft 9, and on the main shaft 9 in the subframe 22. A pump plate 25 is placed between the pump roller 25, the pump cover 27 having a flow path 26 for forming a passage in the pump roller 25, and the subframe 22 and the pump cover 27. It is.

The oil return system includes a pivoting scroll (10) coupled to the drive bush (16) and a main frame (15) which is a side outer wall of the space (29) with a slight space (29) at the face of the main frame (15). Oil return hole (R) leading to the suction chamber (3) along the thickness of the and includes a return hole in each support system or oil flow path.

The oil allocation scheme for the drive system and support system during operation has a direction from bottom to top.

That is, when the main shaft 9 is turned, the pump roller 25, which is a volumetric oil supply pump mounted on the subframe 22, rotates and sends oil to the supply passage 23 of the main shaft 9. The oil flowing into the main shaft (9) is continuously introduced by the centrifugal force of the main shaft (9) and is first supplied to the journal bearing (21B) between the subframe (22) and the main shaft (9), and the rest overcomes gravity and flow path resistance. And some of them climb up the inclined supply passage 24 to lubricate the journal bearing 21A on the contact surface of the main shaft 9 and the main frame 15, wherein the lower journal bearing 21B is lubricated. The lubricated oil returns to oil level (H).

Some of the oil which has been continuously lubricated by the journal bearing 21A lubricates the main thrust bearing 20 through a lubrication hole, and part of the space 29 between the pivot frame of the main frame 15 and the turning scroll 10 Supplied by.

And the remainder which does not flow into the lubrication hole from the supply hole rises to the end of the main shaft (9) to lubricate the journal bearing (21) between the turning scroll (10) and the driving bush (16), and the rest of the shaft pin portion and the driving portion It enters the space 29 between the sieves 16 and is supplied to the space between the pivoting bearings of the journal bearing 21 and the turning scroll 10 to return to the oil level H through most of the oil return holes R. The remainder is lubricated thrust bearing 20 and then flows into the compression chamber 12 along the flow path in the compression chamber 12 of the fixed scroll 11 and the turning scroll 10 and is not discharged together with the refrigerant. Return to H).

Particularly, in the refrigerant compression process that leads to suction, compression, and discharge of the refrigerant by the relative movement of the fixed scroll 11 and the swinging scroll 10, a considerable amount of oil enters into the compression chamber and is discharged together with the refrigerant. This is achieved by creating an oil path into the compression chamber for the formation of an oil film on the contacting motion in 12) and the sealing between the scroll wraps.

That is, the oil that once enters the compression chamber of the compression mechanism part is considered to be discharged together with most of the refrigerant unless there is any other artificial means.

The oil discharge occurs due to the factor of the compression chamber characteristics of the compression mechanism, but the amount varies depending on the operating speed.

For example, in a variable speed scroll compressor in which the operating speed varies by 0.5 to 2 times the rated frequency according to the environment, the oil supply varies according to the operating speed and the frequency band. In the case of the high speed operation, the oil supply amount is increased than the low speed / rated frequency operation, and the amount of oil discharged out of the compressor together with the refrigerant in the compressor increases in proportion to the oil supply amount.

Therefore, in the high-speed operation, the amount of oil remaining in the compressor decreases as the amount of oil and the discharge amount increase together, and when the amount of residual oil reaches a low level below the threshold, insufficient oil supply corresponding to the operation speed is not performed properly. This oil supply failure is not enough oil to be sent to each lubrication part and the contact movement surface decorated around the support system, which causes mechanical wear, such as abrasion on the contact movement surface, bearing restraint, or thermal deformation between parts. Defects appear and affect compressor reliability.

This problem is more serious in variable speed scroll compressors, such as refrigeration and air conditioning cycles, which increase and decelerate up to approximately 0.5 to 2 times the rated operating frequency to cope with the operating environment such as indoor and outdoor temperature and target temperature setting.

As the running speed changes, the speed at which the oil pump turns is the same. This fluctuates the oil supply and there is a remarkable difference in oil supply at low speed and high speed operation. At high speeds, the oil supply is also activated and a large amount of oil follows the spindle. The amount of oil discharged is closely related to the amount of oil supplied.

There are several ways to reduce the amount of oil discharged.

The operating speed is maintained at the rated frequency band. But in a variable speed scroll compressor, this operation is meaningless.

Sufficient oil supply is maintained at the increase and decrease speed while suppressing the discharge amount similarly to the discharge amount generated at the rated frequency band. This is because the faster the speed of operation, the faster the oil circulation and the more sufficient flow is required. However, control of the discharge amount proportional to the oil supply amount remains a problem.

The other is to maintain the oil supply in proportion to the speed while the suction and compression discharge process in the compression chamber with the refrigerant to recover the discharged oil. For example, a method of recovering the oil discharged from the compression chamber together with the refrigerant to the bottom surface using a mechanism such as a capillary tube toward the lower pressure from the discharge chamber in which the discharge pressure is formed.

However, it is difficult to systematically send the oil in the discharge chamber downward, and there is a burden of having to separately install an additional device dedicated to oil recovery.

In the variable speed scroll compressor, the oil lubrication amount and the discharge amount are proportional to the operation speed, resulting in a loss.

The application of several methods has led to the inevitable application of new devices related to the discharge and control of the discharge volume or lack of sufficient flow required for variable speed scroll compressors.

Setting aside a dedicated discharge chamber or a retrieval device for collecting oil already discharged in the discharge passage has no value beyond a simple attachment irrelevant to the dynamic performance of the compression mechanism and lowers the economy.

However, if there is no oil recovery device in the variable speed scroll compressor, especially in high speed operation, the amount of lubrication and discharge rate increase rapidly, and when the amount reaches the low level beyond the threshold, it is not possible to maintain enough oil level for lubrication. Due to this, mechanical failures such as wear of the contact surface of the drive system, restraint of bearings, or heat deformation between parts may be caused, which affects the performance of the compressor, which leads to a problem of deteriorating reliability.

The present invention has been provided by how the oil discharged during compressor operation can be reliably reduced without additional equipment.

Therefore, an object of the present invention is to recover the oil from the compression chamber consisting of the scroll scroll of the fixed scroll and the swing scroll in which the oil discharge occurs, without any additional device.

Another object of the present invention is to improve the reliability by recovering oil from the compression chamber through the flow of fluid flow during compressor operation.

1 is a schematic diagram of a scroll compressor.

2 is a swing scroll structure,

(A) a floor plan,

(B) section.

3 is a fixed scroll structure,

(A) a floor plan,

(B) section.

4 is a cross-sectional view of the scroll wrap wire.

5 is a detailed view of portion A of FIG. 4;

6 is a refrigerant flow direction diagram in a scroll wrap.

Figure 7 shows a scroll wrap front surface according to the present invention,

(A) section,

(B) is a perspective view of part B of (a).

8 is a refrigerant flow direction diagram in the scroll wrap according to the present invention.

Figure 9 shows another embodiment of the present invention,

(A) section,

(B) is a perspective view of part C of (a).

10 is a discharge hole structure according to the present invention.

*** Explanation of symbols for the main parts of the drawing ***

2: discharge room 3: suction room

6: Case 9: headstock

10: turning scroll 11: fixed scroll

12: Compression chamber 15: Main frame

16: Drive Bushing 20: Thrust Bearing

21.21A.21B: Journal bearing 22: Subframe

23: Supply passage 24: Inclined supply passage

25: pumping roller 27: pump case

29: space 30.30A: Scroll wrap

31: Tip thread groove 32: Tip thread

40: oil euro 41: discharge ball

The characteristics of the present invention for achieving this object, by converting the rotational movement of the main axis to the rotational movement for a fixed scroll having a scroll wrap of the involute curve through the rotating scroll coupled to the scroll wrap corresponding to the fixed scroll A scroll compressor having a refrigerant compression chamber in relative motion between each wrap;

The oil flow path is formed along the involute curve of the scroll wrap so that the oil can be discharged from the high pressure side to the low pressure side at the upper end of each of the fixed scroll and the rotating scroll.

Optionally, the oil flow passage is formed on one side of the fixed scroll wrap or the swing scroll wrap.

Another feature of the present invention, through the rotating scroll coupled to the fixed scroll having a scroll wrap on the involute curve and the corresponding scroll wrap to form a compression chamber in the relative motion between each of the wraps, the top surface of the wrap on the involute curve A scroll compressor comprising this tip seal groove;

It characterized in that the oil flow path is formed along the surface of the involute trajectory made by the tip chamber groove of the fixed scroll and the swing scroll.

Optionally, the oil channel is formed by selecting a bottom surface of the tip seal groove.

Optionally, the oil flow path further comprises a discharge hole penetrating the end surface of the fixed scroll and the turning scroll and the tip seal groove.

Optionally characterized in that the cross section of the oil passage is treated in a square.

Optionally characterized in that the cross section of the oil channel is treated with a sphere including a hemispherical shape.

In this way, if the oil flow path is placed on the upper surface of each scroll lap that makes the compression chamber by the contact between the fixed scroll and the rotating scroll lap, some of the oil passing through the contact movement surface between the scroll laps is sent to the low pressure side without additional equipment. You can get results that reduce the amount of oil that goes out together.

An embodiment of the present invention will be described with reference to the drawings.

7 is a schematic view of the lap contact surface of the fixed scroll and the revolving scroll, Figure 9 is a schematic view of the contact surface of the scroll wrap in a different form.

In the embodiment, the main part has an oil passage 40 on the top surface of the scroll wraps 30 and 30A of the involute curve of the compression chamber 12 made by the fixed scroll 11 and the turning scroll 10.

This oil flow path is in the form of one or more complex flow paths near the top surface of the scroll wraps 30 and 30A of the swinging scroll 10 or the fixed scroll 11, or is optionally defined for each scroll, on the end of each scroll. As shown in Figure 10 may have a separate discharge hole (41).

However, the oil flow paths 40 corresponding to the top surface trajectories of the scroll wraps 30 and 30A on the involute curve of the turning scroll 10 and the fixed scroll 11 are formed so that each scroll wrap 30 and 30A is formed. The basic structure is that the oil which is supplied to the surface of the contacting part and the remaining oil can flow from the high pressure side to the low pressure side.

Another form of making the oil flow path 40 in the scroll wraps 30, 30A is that each scroll wrap 30, 30A of the swing / fixed scroll 10, 11 or one of the scroll wraps has a tip seal 32. If it is to form a new oil passage 40 in the limited tip seal groove (31).

The oil channel 40 is formed to process one more space through which the oil can flow along the bottom surface of the tip thread groove 31, and the tip thread 32 is driven in the team thread groove 31 above. The flowing oil is to the extent that the oil flow path (40).

The oil channel 40 formed in each scroll wrap may have any shape irrespective of the shape of the scroll wrap, or the cross section of the oil channel 40 may be applied by selecting a shape such as square, triangle, notch, etc. from a sphere. have.

In this case, the oil flow path 40 is formed between the contact surfaces between the counter wraps of the scroll wraps 30 and 30A.

When the top surface of the scroll wrap 30, 30A is flat, the oil passage 40 is dug from the surface, and the tip thread 32 when the top surface of the scroll wrap 30, 30A consists of a tip thread. While in contact with the mating side, the oil passage 40 is located in the tip chamber groove 31 in a non-exposed manner.

In this way, if various types of oil flow paths are defined along the upper surface of the involute curve of each scroll lap to create a passage for lowering the oil in the compression chamber, the fixed scroll and the turning of the oils going out to the discharge chamber along with the discharge refrigerant The oil remaining on the lap surface of the scroll can be quickly sent to the low pressure side oil surface through the oil channel to reduce the amount of oil discharged. Specific actions are as follows.

As the main shaft 9 rotates, the turning scroll 10 rotates along, causing a relative movement between the fixed scroll 11 and the scroll wrap 30, 30A to compress the refrigerant. At this time, the wear of the oil film on the contact surface between the scroll wraps 30 and 30A is reduced, and the sealing against radial and tangential leakage depends entirely on the sufficient oil supply pumped below. Therefore, when the scroll wrap forms the compression chamber, oil is supplied to the compression chamber 12 sufficiently and the compressed refrigerant is sent to the discharge chamber, so the oil comes with the discharged refrigerant in the compression chamber. Of course, the amount of oil escaped during high speed operation in a variable speed scroll compressor is larger. In quantitative terms, it is proportional to the driving speed.

The oil which has risen to the compression chamber along the main shaft is lubricated and sealed between the scroll wraps 30 and 30A, and part of the oil is discharged into the discharge chamber together with the refrigerant, and part of the oil is collected at the contact surface between the scroll wraps.

The compression chamber, which is represented by the relative motion of the scroll wraps 30 and 30A, collects from the outside to the center and has a movement that opens again. The oil also flows through the space made by the scroll wrap and the contact surface of each wrap. Therefore, the oil flow distribution shows the largest distribution at the center and the smallest at the outside. Since this region is a portion where the refrigerant gathers and exits to the discharge port 18 of the fixed scroll 11, the oil separated from the refrigerant is also collected and thus will have a higher flow rate distribution.

This is a flow distribution in the compression chamber represented by the relative movement of the scroll wraps 30 and 30A, but the flow distribution in the upper end of the scroll wrap does not flow in the inner high pressure side but appears in the outer low pressure side.

This phenomenon can be seen through the leakage path according to the refrigerant flow when the tip seal is applied to the scroll wrap in the compression chamber of the general scroll compressor as shown in FIG. The flow is largely classified into four directions.

Radial X, leakage occurring between the fixed scroll 11 and the tip chamber 32 of the rotating scroll 10 and the bottom surface of the fixed and rotating scroll 11 and 10 on the opposite side thereof.

Radial X ', leakage through the gap between the tip chamber groove 31 and the tip chamber 32 of the fixed scroll 11 and the swing scroll (10).

Leakage flowing along the involute of the lap through the gap between the tip chamber groove 31 and the tip chamber 32 of the fixed scroll 11 and the turning scroll 10 and the high pressure section low pressure section direction Y.

It is the flow in each X.X'.Y.Z direction, such as the leakage which flows along the lap tangential direction of the wrap tangential direction Z, the fixed scroll 11, and the turning side scroll tangential of the turning scroll 10. As shown in FIG.

When the oil flow path 40 is formed in the scroll wrap 30 and 30A having the structured tip thread, the flow path has a refrigerant leakage flow of X1.X'1.Y1.Z1 as shown in FIG. There is no difference in flow with or without.

However, if there is an oil passage 40 in the scroll wraps 30 and 30A, there may be a flow of refrigerant flowing along the lap curve in the direction of Y / Y1, that is, the gap between the tip seal groove 31 and the tip seal 32. When the flow of oil appears directional in the same direction.

Continuously, the directional refrigerant flow has directionality in the inward direction from the high pressure part in the outward direction to the low pressure part in the outward direction, and is adapted in the same direction as the flow chart of the oil, which is the tip seal groove 31 and the outer intake port located near the discharge port 19. 14) Since the tip seal groove 31 of the lap located in the vicinity is provided with a pressure close to the discharge pressure and the suction pressure, respectively. That is, in the scroll wraps 30 and 30A, a large pressure difference is formed in the tip thread groove 31 along the involute of the scroll wrap, and the tip thread 32 of the turning scroll 10 and the fixed scroll 11 is In the state of contact movement with the surface part of the other side and oil filled in this surface part, the oil shows the same directionality of refrigerant movement and the flow of the flow.

When the oil passage 40 is installed in the tip seal groove 31 of the scroll wrap and the discharge hole 41 is installed at the end of the wrap and communicates with the edge of the tip seal groove 31, the tip seal groove of the outermost wrap The oil reaching 31 is discharged to the outside of the compression chamber 12 through the discharge hole 41.

The flow rate and discharge rate of the oil is proportional to the operating speed of the compressor. That is, in the high speed operation, the amount of oil entering the compression chamber 12 increases, which means that the amount of oil accumulated in the center of the high pressure lap and the low pressure lap end is increased, and thus the discharge amount increases.

As shown in FIG. 9 in which the oil flow path 40 is formed in a flat scroll wrap without the tip seal groove 31 at the upper surface of the scroll wrap 30, 30A, the leakage path of the refrigerant may vary due to the difference in space occupied by the tip seal. have. Basically, however, there is no difference in the flow of the flow, which is expressed in the radial direction X2, the high pressure section → the low pressure section direction Y2, and the wrap tangential direction Z2.

Therefore, except for the flow variable that does not apply to the tip chamber, the flow of Y2 in the direction of the high pressure part to the low pressure part of the flow of the refrigerant flow basically appears along the oil path 40 even in the scroll wrap (30) (30A) without the tip thread. This maintains the flow of oil in the same way as a scroll wrap with a tip seal groove.

The oil flow path 40 formed on the top surface of the scroll wrap 30, 30A has a rectangular shape. triangle. It can be made by processing in various forms such as notched shape, and since the flow of oil is basically due to the pressure difference on the oil surface made by the oil flow path of the scroll wrap, the oil flow shape has little influence.

On the other hand, the application of the additional device for recovering the oil already discharged from the scroll compressor is functionally inadequate and not economical in many ways because of the long flow path. appear. The present invention is directed to the low pressure side along the scroll wrap during operation of the compressor in the compression chamber in which the oil discharge occurs mainly in the compression chamber where the oil discharge occurs, to the various problems appearing in the oil recovery center Reduces the amount of oil that collects in and exits the discharge chamber.

The present invention obtains a new oil return path from the scroll wrap forming the compression chamber without increasing the amount of oil discharge which increases or decreases according to the operating speed in the scroll compressor, and directly sends the oil along the scroll wrap to the low pressure side. Machinability compared to other devices provided to reduce the amount of outgoing oil, thereby preventing the compressor from being deteriorated due to oil shortages, and to recover the oil discharged with the refrigerant. It is economical because it is easy to install and can be made into the shape of scroll wrap without additional parts, and it is more effective in variable speed scroll compressor.

Claims (3)

The rotating scroll combined with the scroll lap corresponding to the fixed scroll having the scroll lap on the involute curve forms a compression chamber with relative movement between the laps, and the scroll top of the lap on the involute curve includes the tip thread groove. In a compressor; The oil discharge reduction structure of the scroll compressor, characterized in that the oil flow path is formed on the bottom surface of the tip seal groove along the involute trajectory surface of the fixed scroll and the tip seal groove of the swing scroll. The method of claim 1, The oil flow path further reduces the oil discharge of the scroll compressor, characterized in that it further comprises a discharge hole penetrating the end end of the fixed scroll and the rotating scroll and the tip seal groove. For the fixed scroll having the scroll wrap of the involute curve, the rotational movement of the main shaft is converted into the turning motion, and the rotating scroll combined with the scroll wrap corresponding to the fixed scroll forms the refrigerant compression chamber by the relative motion between each wrap. In a scroll compressor; Oil discharge reduction structure of the scroll compressor, characterized in that the oil flow path is formed along the involute curve from the center portion to the top end of the scroll wrap of the fixed scroll and the revolving scroll.